Pump with an electrodynamically supported impeller and a hydrodynamic bearing between the impeller and the stator

ABSTRACT

A pump includes an impeller, a stator, and a plurality of magnets forming bearing poles coupled to a selected one of the stator or the impeller. The pump further includes a plurality of shorted coils coupled to the other of the stator and the impeller. The plurality of bearing poles and shorted coils co-operate to form an electrodynamic bearing during rotation of the impeller. The electrodynamic bearing supports the impeller either axially or radially during operation of the pump. Hydrodynamic bearing surfaces are provided for generating a hydrodynamic bearing between the impeller and stator. The plurality of magnets may comprise a plurality of distinct magnetic elements or a single element comprising a plurality of distinct magnetic domains. The plurality of distinct magnetic elements or domains may be arranged to form a Halbach array.

CROSS-REFERENCE TO RELATED APPLICATIONS

This application is a continuation of application Ser. No. 10/007,803filed Nov. 13, 2001 now U.S. Pat. No. 6,644,378.

FIELD OF THE INVENTION

This invention relates to the field of pump design. In particular, thisinvention is drawn to bearings supporting pump impellers.

BACKGROUND OF THE INVENTION

Traditional dynamic pumps have a pumping component and a drivecomponent. The pumping component includes an impeller supported bymechanical contact bearings. Mechanical energy is transferred from thedrive component to the impeller of the pumping component through ashaft. A shaft seal in the pumping component permits rotation of theshaft while preventing leakage around the shaft.

Shaft seals are prone to failure due to continuous mechanical wearduring operation of the pump. Mechanical contact bearings supporting theimpeller are also prone to failure. The pumped fluid may adverselyaffect the life expectancy of the bearings. For example, the mechanicalcontact bearings and seal may be particularly susceptible to failurewhen in contact with caustic materials. Alternatively, the bearings maydamage the fluid being pumped. Contact bearings, for example, may resultin increased levels of hemolysis and thrombosis in blood pumpapplications.

Some recent pump designs have integrated the pump and drive componentsinto a single unit so that the pump impeller is also the motor rotor,thus eliminating the need for a transmission shaft to supply power tothe impeller. Such designs eliminate the need for shaft seals. Examplesof pumps with combination impeller/rotors may be found in U.S. Pat. No.5,607,329 of Cho, et al. (marine propulsor), U.S. Pat. No. 5,695,471 ofWampler and PCT publication WO 99/12587 of Woodard, et al. (bloodpumps).

Some of these pump designs also incorporate passive magnetostaticbearing (PMB) or active magnetic bearing (AMB) systems or othernon-contacting bearing mechanisms (e.g., hydrodynamic bearings) in lieuof mechanical contact bearings to stabilize the impeller axially and/orradially. Without mechanical bearings to wear out, these non-contactingbearing mechanisms eliminate disadvantages associated with themechanical contact bearings.

PMB architectures are characterized by the use of opposing sets ofpermanent magnets arranged to repulse each other. The bearings are thusmagnetostatic bearings. For example, Wampler discloses radialmagnetostatic bearings using concentric sets of stacked magneticelements of alternating magnetization. Radial impeller support isprovided by locating one set of magnetic elements in the stator andanother set in the impeller such that the first and second sets areconcentric and coaxially aligned. The concentric stacks of permanentmagnets co-operate to form a radial PMB. The repulsive magnetostaticforces are substantially constant independent of pump speed.

One disadvantage of this design is that each magnet in a stack isconstantly exposed to a significant de-magnetizing field due to theclose proximity of the adjacent magnets in the stack. Anotherdisadvantage of this design is that the use of axially alternatingmagnetic rings results in a number of points of axial metastabilitywhich may create pump control or efficiency issues. The passivemagnetostatic bearings can create significant axial bearing load issuesfor impellers with a radial PMB. Similarly, impellers with an axial PMBmay suffer from significant radial bearing load issues. These loadingforces result in a less power efficient pump.

Active magnetic bearing systems are characterized by the use ofpermanent magnets, electromagnets, position feedback information, andcontrollers as illustrated by U.S. Pat. No. 6,227,817 B1 of Paden. Theimpeller is stabilized with respect to one or more axes by a controlledinteraction between the magnets and electromagnets. The electromagnetsare dynamically controlled by the controller based on the positionfeedback information and sophisticated control algorithms. Position ofthe impeller is controlled by varying the current through the windingsforming the electromagnets. Due to the dynamic nature of the controlelements, the impeller position can be controlled with greaterprecision. In addition, active magnetic bearing systems can beincorporated into the drive such that the electromagnets are serving toboth drive and support the rotor.

The PMB system does not require position feedback or power to operate.In contrast, an AMB will fail in the event of a power interruption,computational error, sensing error along any axis, etc. AMB systems arethus inherently unstable. AMB systems also require significantcomputational resources for position control. The use of AMB systemsintroduces multiple points of failure which may be unacceptable for somepump applications (e.g., implantable pumps).

SUMMARY OF THE INVENTION

A pump includes an impeller, a stator, and a plurality of magnetsforming bearing poles coupled to a selected one of the stator or theimpeller. The pump further includes a plurality of shorted coils coupledto the other of the stator and the impeller. The plurality of bearingpoles and shorted coils co-operate to form an electrodynamic bearingduring rotation of the impeller. One of the stator or impeller includeshydrodynamic bearing surfaces for generating a hydrodynamic bearingbetween the impeller and stator.

In various embodiments, the electrodynamic bearing supports the impellereither axially or radially during operation of the pump. The pluralityof magnets may comprise a plurality of distinct magnetic elements or asingle element comprising a plurality of distinct magnetic domains. Theplurality of distinct magnetic elements or domains may be arranged toform a Halbach array.

Other features and advantages of the present invention will be apparentfrom the accompanying drawings and from the detailed description thatfollows below.

BRIEF DESCRIPTION OF THE DRAWINGS

The present invention is illustrated by way of example and notlimitation in the figures of the accompanying drawings, in which likereferences indicate similar elements and in which:

FIG. 1 illustrates one embodiment of a centrifugal pump.

FIG. 2 illustrates one embodiment of an impeller with a radial passivemagnetic bearing (PMB).

FIG. 3 illustrates one embodiment of an impeller with a radialelectrodynamic bearing.

FIG. 4 illustrates an electrical model of a shorted coil illustrated inFIG. 3.

FIG. 5 illustrates an electrical model of a shorted coil where coilportions are at 180° mechanical angle about the spindle axis.

FIG. 6 illustrates an impeller hub having magnetic vectors organized toform a Halbach array through individual elements or individual magneticdomains.

FIG. 7 illustrates one embodiment of an impeller configured for an axialflux gap motor and an axial electrodynamic bearing.

FIG. 8 illustrates one embodiment of an impeller configured for an axialflux gap motor and a radial electrodynamic bearing.

FIG. 9 illustrates one embodiment of an impeller configured for a radialflux gap motor and an axial electrodynamic bearing.

FIG. 10 illustrates one embodiment of an impeller configured for aradial flux gap motor and a radial electrodynamic bearing.

FIG. 11 illustrates repulsive forces contributed to an impeller by asingle shorted coil when the coil is configured for induction from asingle bearing pole at a time.

FIG. 12 illustrates repulsive forces contributed to an impeller by asingle shorted coil when the coil is configured for induction by twobearing poles at a time.

FIG. 13 illustrates repulsive forces contributed to the impeller by asingle shorted coil when the coil is configured for induction by aplurality of bearing poles at a time.

FIG. 14 illustrates an impeller with a radial electrodynamic bearing andan axial hydrodynamic bearing surface.

DETAILED DESCRIPTION

FIG. 1 illustrates one embodiment of a centrifugal pump 100 providingradial support for the impeller 110 through the use of magneticbearings. The pump includes a top housing portion 120 and a bottomhousing portion 130. When assembled the top and bottom housing portionsdefine a volute pumping chamber 122. Rotation of impeller 110 drives theworking fluid from the pump inlet 150 to the pump outlet 160.

Centrifugal pump 100 utilizes an axial flux gap motor architecture. Whenassembled, the top and bottom housing portions serve as a motor stator.The motor windings 140 are disposed in the stator. The impeller servesas a motor rotor and includes a plurality of permanent magnets formingmotor poles. The motor poles are arranged to co-operate with the motorwindings to drive the impeller and thus achieve a pumping action. Backiron 170 serves to concentrate the flux generated by the windings 140.

The pump further includes a spindle protruding from the base of thepumping chamber. The spindle is not illustrated in FIG. 1 to avoidobscuring the remainder of the pump. The impeller 110 rotates about thespindle. The spindle thus forms a part of the stator. In thisembodiment, the impeller 110 contains one portion of the radial magneticbearing. The spindle carries another portion of the radial magneticbearing. The impeller and spindle bearing portions co-operate to provideradial support for the impeller.

FIG. 2 illustrates one embodiment of an impeller 210 with a radialpassive magnetic bearing using concentric stacked permanent magnets. Oneset of ring or disk shaped permanent magnets 270 is retained by thestator/spindle 250 and a ring shaped set 220 is retained by the impeller210. The impeller portion of the magnetic bearings are disposed withinthe impeller such that they are coaxially aligned with the axis ofrotation 290 and encompass the center of the impeller. The stator set issupported by the spindle 250 protruding from the base of the volute. Inthis embodiment, the impeller also includes permanent magnets (e.g.,motor pole 202) disposed within the blades (e.g., 230). The latter setof permanent magnets co-operate with the motor windings to drive theimpeller.

Each stacked set of magnets is arranged so that they form a coaxiallyaligned set of magnetic cylinders of alternating opposing magnetizationalong the axis of rotation. If a selected magnetic element 222 in astack has a magnetic vector parallel to the axis of rotation 290 andpointing a first axial direction (an “N” orientation), the adjacentmagnet(s) (e.g., 224) have a magnetic vector parallel to the axis ofrotation 290 and pointing 180° from the first axial direction (an “S”orientation). Each magnetic element in stack 220 is separated from itsneighbor by a flux re-directing separator ring 226. Similarly, eachmagnetic element in stack 270 is separated from its neighbor by aflux-redirection separator disk or ring. In one embodiment, theseparators are ferrous. The separators serve to re-direct andconcentrate the magnetic flux radially. Proper alignment of the inner270 and outer 220 stacks results in mutually repulsive forces betweenthe inner and outer cylinders.

The impeller is radially supported by passive magnetostatic forcesbetween the spindle set of magnets about which the impeller set of ringshaped magnets rotates. The concentric sets of stacked rings form aradial magnetostatic bearing and provide substantially the same radialforce regardless of impeller rotational speed.

One disadvantage of this design is the change in magnetic flux along theaxis of rotation 290. The magnetic field varies sharply because adjacentrings have magnetic vectors that have a 180° phase difference. Thesharply varying magnetic field results in axial loading and multiplepoints of metastability. Another disadvantage of this design is thatindividual magnetic rings are continuously subjected to thedemagnetizing fields of neighboring magnetic rings. Finally, due to theuse of a magnetostatic bearing, any loading forces created by thebearing are present substantially independently of the impellerrotational speed. PMBs, however, may be designed to be inherently stableat least along a single axis. No power or control signals are requiredfor the bearing to maintain integrity about the chosen axis.

One set of magnets may be replaced with electromagnetic windings toachieve the same affect. The windings are energized to produce amagnetic field and thus achieve the same effect as passive magneticbearings. Depending upon the design, the electromagnetic windings mayachieve control along more than a single axis. This approach requiresgreater computational capabilities because the position of the impellermust be monitored to determine the extent to which the windings shouldbe energized to accommodate various loading forces. This type of bearingis referred to as an active magnetic bearing (AMB). Active magneticbearings are inherently unstable. Power and proper control signals arerequired at all times for the bearing to maintain integrity.

An alternative magnetic bearing design uses a set of permanent magnetsand a set of shorted coils. This magnetic bearing relies on theinteraction between a plurality of permanent magnets and shorted coilswhen the impeller is rotating. The shorted coils are arranged such thatthe permanent magnets induce a current in the shorted coils due torelative movement between the magnets and the coils when the impeller isrotating. The current in the shorted coils generates a magnetic fieldthat tends to oppose the magnetostatic field of the inducing permanentmagnet. Instead of a passive magnetostatic bearing or an active magneticbearing, the bearing mechanism results from self-induced electrodynamicforces. Such magnetic bearings are referred to as electrodynamic or eddycurrent bearings. The bearings are still “passive” in nature given thatno external control signals or power is required to maintain integrityof the bearing.

FIG. 3 illustrates an alternative embodiment of an impeller 310incorporating a radial electrodynamic bearing. The impeller includes aplurality of permanent magnets 320 for the radial bearing as well aspermanent magnets 302 forming the drive magnets. The bearing magnets 320should be positioned so as not to interfere with the pump drivecomponent formed by the motor windings and the drive magnets 302. In theillustrated embodiment, the drive magnets and bearing magnets aredisposed within blades (e.g., 330) of the impeller 310. As the impellerrotates about axis 390, the bearing magnets create a time varyingmagnetic field that induces currents and corresponding repulsivemagnetic forces in the shorted coils 370 within the spindle 350. Thespindle forms a portion of the motor stator 380. In one embodiment, eachshorted coil is wound around ferrous material 372.

FIG. 4 illustrates an electrical model 480 of a single shorted coil ofthe radial bearing of FIG. 3. The electrical model illustrates thecurrent and voltages induced in the shorted coil by the time-varyingmagnetic field created by the rotating impeller 310. As the impellerrotates about axis 490, a voltage differential develops between coilportion 482 and 484. The voltage differential results in a current, I,and a corresponding magnetic field which opposes the inducing magneticfield thus establishing the radial magnetic bearing.

When the impeller is rotating, only one side of each coil of coilassembly 370 is exposed to inducing bearing poles. Generally, currentwill be flowing in each coil as long as the impeller is rotating.

FIG. 5 illustrates an electrical model 580 of a single shorted coil of aradial bearing when the coil portions 582, 584 are at 180° mechanicalangle from each other. A shorting disk or ring (electrical model element560) may be used to couple coil portions at 180° from each other aboutthe coil assembly. Assuming bearing poles of the same magnetic vectorare also located at 180° mechanical angle, the net induced current, I,will be zero when the impeller is properly centered (V1=V2) because thesame voltage is induced in each coil portion. As the impeller rotationalaxis 590 is displaced from the central axis of the spindle 586, avoltage differential develops (i.e., V1≠V2) thus creating a non-zerocurrent. The generated current is a function of the pitch of the shortedcoils, rotational speed, strength of the bearing magnets, amount ofdisplacement of the impeller, and the impedance, Z, of the shortedcoils.

One characteristic that describes the drive component of a pump motor isthe number of poles associated with the rotor. Each pole represents aconcentration of magnetic flux. Each pole may be a single magnet or aplurality of magnets arranged to provide a resultant magnetic fluxvector. The motor windings are electrically activated to repulse orattract the poles, thus resulting in rotation of the motor rotor. Eachmechanical cycle (i.e., 360° rotation) for the rotor will result in oneor more electrical cycles depending upon the number of pole pairs. Afour pole motor, for example, experiences two electrical cycles for eachmechanical cycle (4 poles/2 poles per set).

The permanent magnets and shorted coils of the electrodynamic bearingare discussed independently of any magnets or windings used in the drivemechanism for the pump. Magnets used for the drive component of the pumpare referred to as drive magnets or motor poles. Magnets used for themagnetic bearing are referred to as bearing magnets or bearing poles.Unless noted otherwise, subsequent use of the terms “magnets” and“coils” is referring to their use in the impeller bearing.

Each bearing pole may comprise a single magnet or a plurality ofmagnets. In one embodiment, the bearing poles have been arranged to forman “undulating magnet” or Halbach array. One advantage of a Halbacharray is that the magnetic flux tends to be concentrated on a selectedone of the interior or exterior of a cylindrical Halbach array or onlyon one side of a linear Halbach array. The individual poles making upthe Halbach array also tend to result in a more sinusoidal magneticfield. Although the magnetic vectors defined by the Halbach array havedifferent orientations, they need not be defined by completely distinctmagnets. For example, a Halbach array may be created by creating domainsof magnetization within a single element. In one embodiment, the Halbacharray is created by magnetic strips of sintered NdFeB.

FIG. 6 illustrates the permanent magnet “hub” of a magnetic bearingcomprising a Halbach array. The Halbach array of hub 620 is formed usingseparate magnetic elements wherein the magnetic vectors within eachelement are substantially the same throughout. The Halbach array of hub630 is formed by varying the magnetization (i.e., individual magneticdomains) within a given element. Although each domain within hub 630 mayhave magnetic vectors substantially the same throughout, the individualdomains may have magnetic vectors significantly different from eachother within the same element. Individual domains within the samemagnetic element are magnetized such that the domains collectively forma Halbach array.

FIG. 7 illustrates one embodiment of an impeller 710 configured for anaxial flux gap motor and an axial electrodynamic bearing. The permanentmagnets forming the bearing poles may be coupled to a selected one ofthe stator or the impeller. The shorted coils are located with the otherof the stator or the impeller. In the illustrated embodiment, themagnets forming bearing poles 720 and the magnets forming motor poles730 are disposed within vanes 740 of the impeller 710. Disk shapedimpeller 710 includes a plurality of channels 760 for moving the workingfluid of the pump. In the illustrated embodiment, each channel is formedon only one face of the impeller so that the channels do not extend toor connect both faces of the impeller. The axial flux gap motorarchitecture and the axial electrodynamic bearing design indicate thatthe axis of magnetization of the motor poles and the bearing poles areparallel to an impeller axis of rotation.

In the illustrated embodiment, the bearing poles 720 are distinct fromthe motor poles 730. The bearing and motor poles do not have anymagnetic elements in common. The number of bearing poles may be lessthan, equal to, or greater than the number of motor poles when thebearing poles are distinct from the motor poles.

In an alternative embodiment, the bearing poles and motor poles rely onthe same magnetic elements. One end of each magnet forms a motor polefor the motor drive component and the other end of the magnet serves asa bearing pole for the impeller support. This might be the case, forexample, with an axial flux gap motor having an axial electrodynamicbearing or a radial flux gap motor having a radial electrodynamicbearing. Given that one end of the magnets serves as a motor pole andthe other end serves as a bearing pole, the motor will typically belimited to stator windings only at one end of the magnets.

Although the bearing poles 720 are indicated as being closer to theinner periphery of the impeller while the motor poles are located closerto the outer periphery of the impeller, other embodiments are possible.For example, in one embodiment the pump motor and electrodynamicbearings architecture is defined such that poles 720 are the motor polesand poles 730 are the bearing poles. In this alternative embodiment, themotor poles are closer to the inner periphery of the impeller while thebearing poles are closer to the outer periphery of the impeller.

FIG. 8 illustrates one embodiment of an impeller 810 configured for anaxial flux gap motor and a radial electrodynamic bearing. The axis ofmagnetization of the motor poles 830 is parallel to the impeller axis ofrotation, but the axis of magnetization of the bearing poles 820 areperpendicular to the impeller axis of rotation. In this embodiment, thenumber of bearing poles is the same as the number of motor poles. Due tothe use of distinct magnetic elements for bearing and motor poles, themotor architecture may incorporate either a single or dual stator (i.e.,a set of drive windings for each end of the motor poles). Thus, forexample, stator windings may be incorporated into the top and bottomhousing portions to produce a dual stator axial gap motor architecture.

FIG. 9 illustrates one embodiment of an impeller 910 configured for aradial flux gap motor and an axial electrodynamic bearing. The axis ofmagnetization of the motor poles is perpendicular to the impeller axisof rotation, but the axis of magnetization of the bearing poles isparallel to the impeller axis of rotation. In this embodiment, thenumber of bearing poles is not the same as the number of motor poles.Impeller 910 has 8 motor poles 930 and 4 bearing poles 920.

FIG. 10 illustrates one embodiment of an impeller 1010 configured for aradial flux gap motor and a radial electrodynamic bearing. The radialflux gap motor architecture and the radial electrodynamic bearing designindicate that the axis of magnetization of the motor poles and thebearing poles are perpendicular to the impeller axis of rotation. Inthis embodiment, the motor poles and the bearing poles are at opposingends of the same magnets. The motor windings may be located adjacent theouter periphery of the impeller (i.e., poles 1030) or the innerperiphery of the impeller (i.e., poles 1020) depending upon the desiredlocation for the drive portion of the motor. The shorted coils for theradial bearing are located adjacent the periphery not otherwise selectedfor the motor windings.

In the preceding illustrations, the bearing poles were located on theimpeller. In alternative embodiments, however, the shorted coils arecoupled to the impeller while the bearing poles are coupled to thestator. High energy magnets such as samarium cobalt orneodymium-iron-boron (NdFeB) may be used for the motor pole magnets, thebearing pole magnets, or both. Regardless of whether the bearing polesare substantially the same as or distinct from the motor poles, theshorted coils may be arranged to achieve different forces as desired forthe bearing.

For example, each shorted coil may be arranged such that current isinduced predominately by only a single bearing pole at any given pointin time as is the case with the shorted coils of FIG. 3. FIG. 11illustrates the axial repulsive force contributed to an impeller 1110 bya single shorted coil when the coil is configured for induction by asingle bearing pole 1140 at a time. No blades or channels areillustrated in order to more clearly illustrate other features.

Each coil can only exert repulsive forces 1150 on the area of theinducing bearing pole 1140. Thus each coil can produce only a localizedrepulsive force on the impeller 1110. This repulsive force may be usedto counteract any axial loading during pump operation. In thisconfiguration each shorted coil has time varying currents in them at alltimes.

In another embodiment, each shorted coil is arranged such that currentis induced by a selected plurality, k, of bearing poles. In such cases,the coil should be arranged so that the selected plurality of bearingpoles have the same magnetic flux vector (i.e., same polarity ormagnetization vector).

FIG. 12 illustrates the repulsive forces contributed to an impeller by asingle shorted coil when the coil is configured for induction by twobearing poles at a time (i.e., k=2). Each shorted coil is acted uponsubstantially simultaneously by a pair of bearing poles. Examples ofbearing pole pairs at different mechanical angles (α, β, α+β) areillustrated. One pairing of bearing poles (1240, 1242) represents amechanical angle α≈120°. Another pairing of bearing poles (1242, 1244)represents a mechanical angle β≈30°. Yet another combination (1240,1244) represents a mechanical angle α+β≈180°.

The repulsive forces will now be distributed across two bearing polesinstead of one. When the impeller is properly aligned, the bearing polesinduce the same current substantially simultaneously into the shortedcoil. Thus the repulsive force is equally distributed among each bearingpole of the bearing pole pair.

As the mechanical angle between bearing pole pairs increases, thecurrent differential for the same angular displacement also increases.Thus increasing the mechanical angle tends to increase the bearing'seffectiveness. This current differential results in an unequaldistribution of repulsive forces across the bearing poles. The unequaldistribution of force makes it easier for the impeller to be returned tothe correct position in the presence of an opposing restoring force. Thecoils will have time varying currents in them whenever the impeller isincorrectly positioned.

The optimal mechanical angle between bearing poles when each coilinteracts with only two bearing poles at a time is 180° (thesimultaneously inducing bearing poles have the same magnetizationvector). If the electrodynamic bearing is designed so that the samemagnitude of current is induced into the shorted coil by each bearingpole when the impeller is centered, there will be no net current flow inthe shorted coil due to the opposing signs. Zero current flow results inless heat dissipation for the pump which may be particularly desirablein implantable pump applications such as blood pumps. When the impelleris properly centered this implies that the pump will be more energyefficient because energy from the rotating impeller will not be consumedby the magnetic bearing.

FIG. 13 illustrates repulsive forces applied to the impeller by a singleshorted coil when the coil is configured for simultaneous induction by aselected plurality, k, of bearing poles at any given time where k>2. Inone embodiment, each shorted coil is configured so that the selectedplurality of bearing poles (1340, 1342, 1344) are at relativeequidistant mechanical angles. The k bearing poles are thus distributedabout the axis of rotation at mechanical angles of$\frac{2\quad\pi}{k}\quad{radians}\quad{\left( {{i.e.},\frac{360{^\circ}}{k}} \right).}$This distributes the repulsive forces (1350, 1352, 1354) about theimpeller axis of rotation. “Ripples” or variations in the forcessupporting the impeller may be reduced by increasing the number k andconfiguring the shorted coil so that the k selected bearing poles aredistributed in this manner.

The control of an impeller requires control of 6 degrees of freedom ofmotion. The bearings must account for 5 degrees of freedom while 1degree of freedom is allocated to the drive component for handling therotational velocity of the impeller. A radial or axial electrodynamicbearing can be used in conjunction with other bearings for full controlof the impeller. The use of the electrodynamic bearing to reduce thenumber of degrees of freedom over which control must still be exerted,for example, reduces the computational complexity required by an AMB.Alternatively, the electrodynamic bearing may be used with other passivebearing mechanisms. Thus in one embodiment, an impeller is configuredfor both an axial electrodynamic bearing and a radial electrodynamicbearing.

FIG. 14 illustrates one embodiment of an impeller 1410 designed for acentrifugal pump with an axial flux gap motor architecture as indicatedby the configuration of motor poles 1430. The impeller 1410 includes aplurality of bearing poles 1420 (or alternatively shorted coils) for aradial electrodynamic bearing. In this embodiment, the impeller includesa plurality of blades 1450 on one face of the impeller. In addition, theimpeller may have hydrodynamic bearing surfaces 1460 designed togenerate axial or radial hydrodynamic bearings when the bearing becomestoo close to features of the stator such as a diffuser or a volute wall.The hydrodynamic bearings may be realized by providing regions 1460 onone face of the impeller that have tapered surfaces. Instead of “blades”the impeller may use a plurality of channels to move the working fluid.In one embodiment, the channels or blades are located only on one faceof the impeller.

Although the illustrations are directed towards an impeller for acentrifugal pump, the electrodynamic bearing can be used with other pumparchitectures such as axial flow or mixed flow pumps. Moreover, the pumparchitecture may include either radial, axial, or both types ofelectrodynamic bearings. The electrodynamic bearings may be utilized inpumps incorporating either axial or radial flux gap motor architectures.

The use of electrodynamic bearings is an improvement over contactbearings which tend to damage some working fluids such as blood (e.g.,thrombosis, hemolysis). If needed, the impeller may be coated to protectthe impeller and incorporated elements from the working fluid. Theelectrodynamic bearings may also be used for pump applications where theworking fluid is gaseous or otherwise fluid-like (e.g., mixtures) innature. For example, air blowers or fans may benefit from theelectrodynamic bearing due to the lack of any need for bearinglubrication. Given that the bearing is operable only once the rotationalspeed reaches a threshold, the designer may need to incorporatetouchdown bearings or other mechanisms to prevent damage whentransitioning from an “off” state to an “on” state or from rotationalspeeds above the threshold to rotational speeds below the threshold. Forapplications where the pump is designed to run continuously (i.e., bloodpumps), such touchdown bearings may not be necessary as a practicalmatter.

In the preceding detailed description, the invention is described withreference to specific exemplary embodiments thereof. Variousmodifications and changes may be made thereto without departing from thebroader spirit and scope of the invention as set forth in the claims.The specification and drawings are, accordingly, to be regarded in anillustrative rather than a restrictive sense.

1. A pump apparatus comprising: an impeller; a stator; a plurality ofpermanent magnets forming bearing poles coupled to a selected one of thestator and the impeller; and a plurality of shorted coils coupled to theother of the stator and the impeller, wherein the plurality of bearingpoles and shorted coils co-operate to form an electrodynamic bearingduring rotation of the impeller, wherein at least one of the stator andthe impeller includes hydrodynamic bearing surfaces structured togenerate a hydrodynamic bearing between the impeller and stator.
 2. Theapparatus of claim 1 wherein the plurality of permanent magnets iscoupled to the stator and the plurality of shorted coils is carried bythe impeller.
 3. The apparatus of claim 1 wherein the plurality ofpermanent magnets is carried by the impeller and the plurality ofshorted coils is coupled to the stator.
 4. The apparatus of claim 1wherein the electrodynamic bearing forms an axial bearing.
 5. Theapparatus of claim 1 wherein the electrodynamic bearing forms a radialbearing.
 6. The apparatus of claim 1 wherein the hydrodynamic bearingforms a radial bearing.
 7. The apparatus of claim 1 wherein thehydrodynamic bearing forms an axial bearing.
 8. The apparatus of claim 1wherein the plurality of permanent magnets comprises a plurality ofdistinct magnetic elements, each magnetic element corresponding to oneof the bearing poles.
 9. The apparatus of claim 8 wherein the individualmagnetic elements form a Halbach array.
 10. The apparatus of claim 1wherein the plurality of permanent magnets is a single elementcomprising a plurality of distinct magnetic domains, each magneticdomain corresponding to one of the bearing poles.
 11. The apparatus ofclaim 10 wherein the plurality of magnetic domains forms a Halbacharray.
 12. The apparatus of claim 1 wherein the stator further comprisesa spindle about which the impeller rotates.
 13. The apparatus of claim 1wherein the impeller includes a plurality of tapered surfaces forgenerating the hydrodynamic bearing.
 14. The apparatus of claim 1wherein the pump apparatus further comprises a plurality of motor polesfor driving the impeller, wherein the motor poles and bearing poles aredistinct.
 15. The apparatus of claim 14 wherein the number of bearingpoles is distinct from the number of motor poles.
 16. The apparatus ofclaim 1 wherein the plurality of permanent magnets also serve as motorpoles for driving the impeller.
 17. The apparatus of claim 1 wherein atleast one bearing pole further comprises a plurality of permanentmagnets.
 18. The apparatus of claim 1, the pump apparatus furthercomprises a plurality of motor poles for driving the impeller, whereineach of the motor poles has an axis of magnetization substantiallyparallel to an axis of rotation of the impeller.
 19. The apparatus ofclaim 1 wherein the pump apparatus further comprises a plurality ofmotor poles for driving the impeller, wherein each of the motor poleshas an axis of magnetization substantially perpendicular to an axis ofrotation of the impeller.
 20. The apparatus of claim 1 wherein the pumpapparatus is a selected one of an axial flow, a mixed-flow, and acentrifugal pump.